CN110892141A

CN110892141A - Piston for a reciprocating internal combustion engine and reciprocating internal combustion engine

Info

Publication number: CN110892141A
Application number: CN201880051622.3A
Authority: CN
Inventors: P.I.乌尔苏亚托雷斯; M.比尔
Original assignee: Volkswagen AG
Current assignee: Volkswagen AG
Priority date: 2017-08-08
Filing date: 2018-07-24
Publication date: 2020-03-17
Also published as: EP3665378A1; DE102017213831A1; US20200173393A1; WO2019029982A1

Abstract

The invention relates to a piston for a reciprocating piston internal combustion engine, comprising a piston ring carrier (12) with an outer piston crown (16) and with an inner piston crown (18) and a piston skirt (20) extending axially from the inner piston crown (18), wherein the piston skirt (20) has at least one guide surface (22) which is of at least partially arcuate configuration, wherein the at least one guide surface (22) is arranged in the region of the arcuate configuration at a distance from the axially connected piston ring carrier (12) such that a gap (24) results between the piston ring carrier (12) and the guide surface (22), wherein the piston skirt (20) and the piston ring carrier (12) are connected to one another via at least one reinforcing rib (32) which extends transversely over the inner piston crown (18).

Description

Piston for a reciprocating internal combustion engine and reciprocating internal combustion engine

Technical Field

The invention relates to a piston for a reciprocating piston internal combustion engine and to a reciprocating piston internal combustion engine having such a piston, in particular for use in a motor vehicle. In this connection, motor vehicles with such reciprocating pistons are likewise explicitly mentioned.

Background

DE 102015201633 a1 discloses a piston for an internal combustion engine, wherein the piston has a piston ring carrier (Ringträger), referred to as a piston ring region (Ringfeld), and a piston skirt (Kolbenhemd), referred to as a cylinder (Schaft), in order to save weight, the piston has a recess extending between the piston ring region and the cylinder from the outside of the piston to the interior of the piston.

Disclosure of Invention

The invention is based on the object of making available a piston for a reciprocating piston internal combustion engine and a reciprocating piston internal combustion engine which, while being sufficiently rigid, is improved in terms of thermal function and has a low weight.

The solution of this object is achieved according to the invention with the features of the independent claims. Further practical embodiments and advantages of the invention are described in connection with the dependent claims.

The piston for a reciprocating piston internal combustion engine according to the invention comprises a piston ring carrier with an outer piston crown and with an inner piston crown. The outer piston crown is the side which, in the installed state of the piston, faces the combustion chamber and directly delimits the combustion chamber. The inner piston crown is the side of the piston crown which faces away from the combustion chamber in the installed state. Starting from the inner piston crown, a piston skirt extends in the axial direction of the piston and has at least one guide surface which is of at least partially arcuate configuration. In particular, the piston skirt can have two guide surfaces which extend in each case over an arc-shaped section (viewed in the circumferential direction of the piston), for example on opposite sides of the piston. In the case of the piston according to the invention, the at least one guide surface is arranged in the region of the arc-shaped configuration at a distance from the axially connected piston ring carrier, such that a gap results between the piston ring carrier and the guide surface. Direct heat transfer from the piston ring carrier to the arc-shaped region is thereby avoided, which is thermodynamically advantageous. Furthermore, the piston skirt and the piston ring carrier are connected to one another via at least one reinforcing rib which extends transversely over the inner piston crown. In particular, the indirect connection between the piston crown of the piston ring carrier and the piston skirt therefore means that at least one reinforcing rib (in particular two or more reinforcing ribs) extends transversely on the piston crown and that from the (respective) reinforcing rib an element or elements of the piston skirt extend, in particular (at least) a piston pin flange and at least one guide surface. In this case, the part of the piston skirt with the guide surface or guide surfaces and the piston ring carrier can be connected to one another only indirectly via the reinforcing ribs. By means of at least one such reinforcing rib, a locally high rigidity of the piston can be achieved with a minimum of material with simultaneously advantageous thermal properties and a low component weight. It is clear that the thermal decoupling achieved with the piston according to the invention is so good that the piston thermal gap approximately corresponds to the piston installation gap, that is to say that only a slight relative change takes place in view of the gap between the piston and the cylinder wall over the entire characteristic curve and temperature range of the reciprocating piston internal combustion engine. The installation play and thus the piston impact pulse (kolbenaffschlagigimpus) can be kept very small. In addition, an acoustically inconspicuous reciprocating piston internal combustion engine with only a low noise generation is thereby likewise produced. Furthermore, the inclination of the piston can be reduced to a minimum, whereby also low fuel consumption results.

The aforementioned gap between the guide surface and the piston ring carrier is in particular a continuous gap, i.e. it accordingly extends over the entire curved guide surface. In other words, the guide surface is separated from the piston ring carrier over its entire arc-shaped extent by the gap.

In particular, it is advantageous in this context that the guide surfaces are heated by the heat occurring in the region of the piston ring carrier, which can lead to increased friction between the guide surfaces and the cylinder wall as a result of thermal expansion, in particular when the heating of the guide surfaces and the cylinder wall takes place at different rates and/or when this expansion takes place as a result of different materials and different coefficients of thermal expansion, which can lead to piston overlap (Kolben ü bereckung) (that is to say to the fact that the piston diameter is greater than the cylinder diameter) and thus in the extreme case even to the occurrence of what is known as "piston seizure" (kolbenferrer) "or to piston seizure (Verklemmen) in the cylinder.

The reinforcing rib extending transversely over the inner piston crown then represents in particular a reinforcing rib which extends transversely from one outer point of the piston crown to the other outer point of the piston crown. It is preferred here if the reinforcing rib is firmly connected to the inner piston crown over a large part of this extent, preferably over the entire extent, transversely across the inner piston crown. A particularly reliable secant-like (sekanternartig) connection of the reinforcing ribs at the piston can thus be achieved and a rigid overall structure results.

The reinforcing rib extends in this respect, in particular, in a secant manner on the inner piston crown. The term "secant-like" is intended to mean here that the reinforcing rib is not limited to a straight rib design between two outer points of the circumference. The term "secant-like reinforcement rib" in the sense of the present invention also means a reinforcement rib which has an arcuate or other curved course, for example a zigzag course. Likewise, the thickness and height of one or more reinforcing ribs extending transversely to the direction of extension of the reinforcing ribs can vary. Preferably, however, the length of the reinforcing rib extending transversely across the piston crown is greater than the width of the reinforcing rib and/or the height of the reinforcing rib extending in the axial direction of the piston.

It is clear that by the combination of at least one gap between one or more guide surfaces and the piston ring carrier (in particular two gaps between in each case one guide surface and the piston ring carrier) on the one hand and the configuration of at least one reinforcing rib extending transversely on the inner piston crown (in particular two reinforcing ribs, wherein the reinforcing rib is correspondingly associated with a guide surface) on the other hand, the piston according to the invention with low material usage can be designed with high rigidity and nevertheless with low weight with a saving of material, as required. It is clear that the design according to the invention even makes possible the manufacture and use of pistons made of aluminum, which are particularly of reduced weight. It is particularly preferred when the piston according to the invention is made of aluminum in one piece.

In a practical embodiment of the piston according to the invention, the at least one reinforcing rib extends in the middle section in the axial direction from the inner piston to such an extent that the piston pin flange is formed in the reinforcing rib. In this case, the central section is in particular the region in two oppositely disposed guide surfaces.

Preferably, two or more reinforcing ribs, in particular two reinforcing ribs which are designed parallel to one another, extend in the axial direction to such an extent that the piston pin flange is designed accordingly in the reinforcing ribs themselves. Via the piston pin flange, in the case of pistons used in reciprocating piston internal combustion engines, forces are transmitted from the piston to the connecting rod, in particular via the inserted piston pin, in order to drive the crankshaft in a known manner. A material-saving, yet at the same time rigid overall structure can be achieved with one reinforcing rib, two reinforcing ribs or a plurality of reinforcing ribs, by means of which the piston is guided well in the cylinder even in the case of high piston forces, thus making low-loss force transmission possible.

The piston skirt is connected to the piston ring carrier, in particular, via at least one reinforcing rib. Furthermore, a connecting section or a plurality of connecting sections can be provided, which are likewise connected to the piston ring carrier. In this context, reference is made in particular to the design in which two oppositely disposed guide surfaces are connected to one another via two connecting sections to form a frame-like structure and the connecting sections are correspondingly connected at least in part to the inner piston crown. The connecting section can extend here in particular transversely over the diameter of the piston via the piston pin flange. When the piston ring carrier, in particular the inner piston crown of the piston ring carrier, is additionally connected to one connecting section or two connecting sections (in particular in the region of the piston pin flange), the overall rigidity of the piston is further increased or the load on the reinforcing ribs can be reduced, so that a further weight optimization can be achieved by a corresponding design of the reinforcing ribs. The connection can be effected only indirectly via the further element (in particular via the reinforcing rib) and/or directly in such a way that the connecting section is at least partially directly joined to the piston head. In this case, it is preferred if such a connection is limited to a region spaced apart from the outer circumference of the piston, in particular to a central region around one piston pin flange or two or more piston pin flanges.

In order to keep the heat transfer between the piston ring carrier and the guide surface low and nevertheless obtain good strength, the at least one connecting section is preferably joined to the inner piston crown via a smaller surface than the corresponding reinforcing rib.

Alternatively or additionally, the connecting section is connected to the piston crown only in an inner region thereof, that is to say in a region spaced from the outer circumference of the piston, in particular in a region which, in the case of a recess limited by an annular outer edge, is located within the outer edge of the inner piston crown.

As an alternative or in addition, the connecting section extends in particular only over the region surrounding the piston pin flange, for example over a length that is slightly greater than the diameter of the piston pin flange, for example a maximum of 1.1 times, a maximum of 1.2 times or a maximum of 1.3 times the diameter of the piston pin flange, in particular such that the connecting section extends over the piston pin flange and protrudes over both sides with the same length.

The piston pin flange is surrounded in particular by a thickening extending perpendicularly to the axial direction. The thickening is preferably part of a connecting section, which is joined at the inner piston head. It is thus achieved that the contact area between the connecting section and the inner piston crown of the piston ring carrier is limited in surface to the (viewed radially) central region of the piston crown, which is thermodynamically favorable.

As already mentioned, the connecting section can be arranged in particular such that the frame-like structure is formed by two arc-shaped guide surfaces arranged opposite one another and two connecting sections arranged opposite one another. In this case, the two reinforcing ribs are in particular formed on the inside of the connecting section. It is calculated that in this case, a particularly high rigidity of the piston is achieved with good thermodynamic properties. In this case, the forces acting in particular on the connecting section are therefore reduced by means of the reinforcing ribs extending inside. Such a piston can particularly advantageously be made of aluminum in one piece.

An additional weight saving can be achieved in connection with the piston according to the invention when the piston ring carrier has a recess or recesses on the face directed toward the piston skirt, i.e. in the region of the inner piston crown. Such a recess can be limited in particular by an outer edge formed on the outer side of the inner piston crown, preferably by an outer edge which has a constant thickness over the entire circumference of the inner piston crown. One or more recesses may then extend within the outer edge. In other words, in the case of the piston according to the invention, the piston crown thickness can be reduced, in particular by the formation of the recess, and therefore additional weight can be saved.

If at least one reinforcing rib extends transversely through the recess in such a way that it is connected to the inner piston crown over the entire secant-like portion, that is to say the secant-like portion extends completely over two points of the outer edge, a recess on both sides of the reinforcing rib results.

Preferably, two or more reinforcing ribs extend transversely through the recess, in particular completely secant.

By the configuration of the recess or recesses, the thickness of the piston ring carrier extending in the axial direction is reduced, whereby material and weight of the piston are saved.

In a further practical embodiment, the at least one reinforcing rib and/or the at least one connecting section are/is curved, viewed in the longitudinal direction (i.e. in the direction of their extent). By longitudinal is meant the direction in which the reinforcing ribs or connecting sections extend transversely to the axial direction with the greatest extent, in particular the direction of extension of the secant-like sections, which extend transversely across the diameter of the piston.

In particular, the reinforcing rib and/or the at least one connecting section have an omega-shaped and/or curved and preferably outwardly curved course. By the omega-shaped and/or curved, preferably outwardly curved course, an improved bending stiffness of the reinforcing rib and the piston as a whole can be achieved, in particular for taking up forces which are to be transmitted by the piston via the piston pin to the connecting rod.

The reinforcing rib preferably has a course such that, viewed in the longitudinal direction, it merges into the thickened region which surrounds the piston pin flange on the inside, in the region of the piston pin flange, and is arranged at a distance from the connecting section in the outer region of the inner piston crown. Preferably, the thickness of the reinforcing rib is increased on the outside, that is to say in particular at a location where the reinforcing rib is close to and/or adjacent to the outer edge of the inner piston crown.

Preferably, two piston pin flanges are provided at the piston according to the invention, wherein each piston pin flange likewise extends through the reinforcing rib corresponding thereto. It is further preferred that the connecting section and the corresponding reinforcing rib form a unit in the region of the piston pin flange, i.e. the piston pin flange extends without transition through the connecting section and the corresponding reinforcing rib. The forces transmitted between the piston and the connecting rod via the piston pin are thus distributed to the connecting section and the corresponding reinforcing rib, which accordingly provides a common hollow-cylindrical bearing surface for the piston pin.

On the outer side (and optionally also on the inner side) of the or each piston pin flange, in a further practical embodiment, a thickening projecting in the passage direction of the piston pin extends in each case, in particular over the entire circumference of the piston pin flange. The thickened portion preferably extends from the middle section of the inner piston crown and is further preferably formed around the piston pin flange, in particular in the shape of a circular arc. With such a thickening, on the one hand an additional stiffening of the region of the piston pin flange can be achieved and on the other hand the intermediate connecting region of the connecting section can be enlarged.

A further weight saving can be obtained when the at least one guide surface of the piston according to the invention has at least one recess, which reduces the guide surface to two or more partial guide surfaces. In principle, weight can be saved at each guide surface of the piston, when less material is required due to the configuration of the recess or recesses (e.g. in the form of a recess, a cut-out, etc.). It has proven particularly advantageous, however, to design the first guide surface without one or more recesses so that the occurring guide forces can be reliably absorbed and the second guide surface, which is subjected to low loads due to its arrangement in the cylinder, is provided with one or more recesses in order to further reduce the weight. The recess or recesses should be such that the guide surface is divided into partial guide surfaces, which are smaller overall than an opposing guide surface.

In particular, the possibility of reducing the guide surface by the configuration of two partial guide surfaces is mentioned in that an upper first partial guide surface arranged close to the inner piston bottom and a lower partial guide surface further away from the inner piston bottom are configured. Such a configuration of the partial guide surface is possible in particular on the so-called back pressure side of the reciprocating piston internal combustion engine, which is subjected to less load in the installed state of the piston. In this case, the upper partial guide surface is preferably larger than the lower partial guide surface.

The invention also relates to a reciprocating piston internal combustion engine with a piston as described above. In particular, the invention relates to an internal combustion engine with a piston, wherein at least one guide surface has at least one recess which reduces the guide surface to two partial guide surfaces. In this case, the partial guide surface is arranged such that it is arranged on the back pressure side. The back pressure side is defined as the side of the piston which, after passing the top dead center, does not come into contact with the piston during the expansion phase. The side of the cylinder on which the piston rests with the guide surface after bottom dead center during the expansion phase is referred to as the pressure side. On the pressure side, generally higher forces act between the cylinder wall and the piston.

Drawings

Further practical embodiments of the invention are described below in connection with the figures. Wherein:

figure 1 shows a piston according to the invention in a first embodiment in a perspective view,

figure 2 shows the piston according to figure 1 in a side view according to arrow II of figure 1,

figure 3 shows the piston according to figures 1 and 2 in longitudinal section according to section line III-III of figure 1,

figure 4 shows the piston according to figures 1 to 3 in a view from below according to arrow IV of figure 1,

figure 5 shows a second embodiment of the piston according to the invention in a perspective view from below,

figure 6 shows the piston according to figure 5 in a side view similar to the arrow II according to figure 1,

FIG. 7 shows the piston according to FIGS. 5 and 6 in a longitudinal section similar to section line III-III in FIG. 1, and

fig. 8 shows in schematic representation a reciprocating piston internal combustion engine with a piston according to the invention arranged therein.

Detailed Description

In connection with fig. 1 to 4, a first embodiment of a piston 10 according to the invention is first described. The piston 10 shown is made of aluminum in one piece in this embodiment. However, alternatively (not shown) it can also be produced in multiple parts. Independently of this, it can alternatively or additionally likewise be produced from other materials, for example from steel materials.

The piston 10 comprises a piston ring carrier 12, which in this embodiment has a total of four recesses in the form of grooves 14 extending over the outer circumference of the piston ring carrier 12. Three such grooves 14, the first (uppermost), the third and the fourth (lowermost), are so-called ring grooves, which are used for arranging piston rings (not shown) and/or the remaining sealing elements (see fig. 2). The second groove 14 shown (which has a smaller radial depth than the remaining grooves and is optionally an unloading groove.) the piston ring carrier 12 has an outer piston crown 16 which, in the installed state of the piston 10 in the reciprocating piston internal combustion engine, points toward and delimits the combustion chamber, an inner piston crown 18 is formed on the side opposite the outer piston crown 16, which faces away from the combustion chamber in the installed state of the piston 10 in the reciprocating piston internal combustion engine.

As can be seen well in fig. 1 to 3, a piston skirt 20 extends from the inner piston crown 18 in the axial direction of the piston 10. The piston skirt 20 comprises two guide surfaces 22 which are arranged opposite one another and which, viewed in the circumferential direction of the piston 10, extend in each case over an arc-shaped section. The guide surface 22 then extends correspondingly over an arc segment of approximately 60 °. As can be seen well in fig. 2 and 3, the guide surface 22 does not contact the inner piston crown 18, since the guide surface 22 is designed such that a continuous gap 24 is formed between the guide surface 22 and the inner piston crown 18. The height Hs of the gap 24 is then approximately 1-2mm, viewed in the axial direction a (see fig. 3).

The opposing guide surfaces 22 are connected by two connecting sections 26, which extend between the guide surfaces 22. The connecting section 26 extends in each case between the outer ends of the guide surfaces 22, as viewed in the circumferential direction. The connecting sections 26 extend generally parallel to each other and spaced from the center M of the inner piston crown 18. As can be clearly seen in fig. 4, the connecting section 26 is curved and bent outward. As can also be clearly seen in fig. 4, the two guide surfaces 22 and the connecting section 26 extending between the guide surfaces 22 form a frame-like structure.

A piston pin flange 28, which is circular in cross section, is formed in the connecting section 26 for introducing a piston pin (not shown). Starting from the connecting portion 26, an outer thickening 30a and an inner thickening 30b are formed on the outer side and the inner side of the piston pin flange 28, respectively. The thickened

portions

30a,30b extend from the middle section of the inner piston crown 18 over the entire circumference of the round piston pin flange 28.

The connecting section 26 joins only in the middle region at the inner piston crown 18, which extends over the piston pin flange 28 and the thickened

portions

30a,30b, respectively.

Two reinforcing ribs 32 are likewise formed on the piston 10, which, as can be seen in fig. 4, extend transversely on the inner piston crown 18. Such a reinforcing rib 32 is well recognizable in the sectional illustration in fig. 3. Here, it is likewise well recognized that the reinforcement rib 32 is connected to the inner piston crown 18 over its entire extent in the longitudinal direction thereof. In the exemplary embodiment shown, the height of the reinforcing rib 32 extending in the axial direction a approximately corresponds to the depth T of the recess in the section adjoining the outer edge 36 of the inner piston crown 18, so that the reinforcing rib 32 merges on the outside into the outer edge 36.

As can be seen from fig. 4, the reinforcing rib 32 has an omega-like course in the direction of extent, with it being correspondingly bent outward in the central region. The two reinforcing ribs 32 are configured mirror-symmetrically to one another about a mirror axis extending through the center M. In the outer region adjacent to the outer edge 36, the reinforcing rib 32 has a greater thickness. In this embodiment, the thickness of the reinforcement rib 32 is about 9mm in the case of a piston diameter between 70mm and 80mm in the outer section. Preferably, the thickness of the reinforcement rib 32 is between 5 and 30 percent, particularly preferably between 10 and 20 percent, of the piston diameter in the outer region.

The piston diameter of the piston 10 according to the invention is preferably between 40mm and 200 mm, further preferably between 60mm and 150 mm and particularly preferably between 80mm and 120 mm.

The reinforcing rib 32 is configured on the inside of the connecting section 26 and is oriented substantially parallel to the connecting section 26. In the central region, the respective reinforcing rib 32 and the inner thickening 30b form a unit, i.e. they are directly connected to one another, so that a continuous piston pin flange 28 with a hollow cylindrical shape is formed on the inside. In the embodiment shown, the elements accordingly have a thickness D of approximately 20 percent of the piston diameter. Preferably, the thickness D is between 10 and 30 percent of the piston diameter.

In the outer region, reinforcing ribs 32 are formed at intervals from the connecting section 26. Likewise, the reinforcement rib 32 is spaced from the center M of the inner piston crown 18.

The piston ring carrier 12 has a recess 34 on the side facing the piston skirt 20. The recess 34 is formed on the inside of a circular outer edge 36, which extends on the outside over the entire circumference of the piston 12 and has a constant thickness. The recesses 34 are separated from one another by the reinforcing ribs 32 and the connecting section 26. As can be seen in fig. 4, a total of seven regions with recesses 34 result, when it is considered that the recesses 34, which are respectively indicated by two associated arrows, likewise extend over the respective region, which in fig. 4 is covered by the respective outer region of the connecting section 26. Only one associated recess 34 is accordingly designated by the associated arrow.

The shape and geometry of the stiffening ribs 32 in a view perpendicular to the direction of extension of the stiffening ribs 32 can be well recognized in fig. 3. The outer side of the reinforcing rib 32, starting from the inside of the outer edge 36, extends in the transverse direction in the recess 34 and is embodied in the form of an arc between them in such a way that the piston pin flange 28 is enclosed, so that the piston pin flange 28 likewise extends through the reinforcing rib 32.

Fig. 5 to 7 show a second embodiment of the piston 10. For the description of the second embodiment, the same reference numerals are used for identical or at least functionally identical elements, as were used for the description of the first embodiment. The piston 10 according to the second embodiment according to fig. 5 to 7 is constructed identically to the piston 10 according to the first embodiment of fig. 1 to 4, if not described or shown otherwise. Only the differences between the second embodiment and the first embodiment are discussed below.

Likewise, the piston 10 of the second embodiment has a piston ring carrier 12 and a piston skirt 20 extending axially therefrom with two guide surfaces 22 extending over an arc-shaped section. One of the guide surfaces 22 is now divided by the recess 38 into two partial guide surfaces 40,42, namely an upper partial guide surface 40, which is arranged close to the inner piston crown 18, and a lower partial guide surface 42, which is further remote from the inner piston crown 18. The upper partial guide surface 40 has a greater height in the axial direction than the lower partial guide surface 42. The height of the recess 38 extending in the axial direction corresponds approximately to the height of the upper partial guide surface 40 in the exemplary embodiment shown.

Fig. 8 schematically shows a reciprocating piston internal combustion engine with a combustion chamber 44 in the form of a cylinder and a piston 10 arranged therein. The piston 10 is connected to a crankshaft 48 by means of a connecting rod 46. The piston 10 according to the second embodiment described above is arranged in the combustion chamber 44 in such a way that the guide surfaces with partial guide surfaces 40,42 are arranged on the back pressure side 50 and the continuous guide surface 22 is arranged on the pressure side 52. The pressure side 52 corresponds to the side against which the piston 10 rests with the continuous guide surface 22 after passing the top dead center (OT) during the expansion phase (i.e., to the left in fig. 8), when the crankshaft 48 rotates clockwise in the direction of the arrow 54.

The features of the invention disclosed in the drawings and in the claims can be essential both individually and in any desired combination for the realization of the invention in its various embodiments. The invention may be varied within the scope of the claims and taking into account the knowledge of the person skilled in the art in charge.

List of reference numerals

10 piston

12 piston ring carrier

14 groove (concave)

16 outer piston top

18 inner piston top

20 piston skirt

22 guide surface

24 gap

26 connecting section

28 piston pin flange

30a outer thickened portion

30b inner thickened part

32 reinforcing rib

34 recess

36 outer edge

38 recess

40 upper part of the guide surface

42 lower part of the guide surface

44 combustion chamber

46 connecting rod

48 crankshaft

50 back pressure side

52 pressure side

Arrow 54 (rotating direction)

Claims

1. A piston for a reciprocating piston internal combustion engine, comprising a piston ring carrier (12) with an outer piston crown (16) and with an inner piston crown (18), and a piston skirt (20) extending in the axial direction from the inner piston crown (18), wherein the piston skirt (20) has at least one at least partially arc-shaped guide surface (22),

it is characterized in that the preparation method is characterized in that,

the at least one guide surface (22) is arranged in the region of the arc-shaped configuration at a distance from the axially connected piston ring carrier (12) such that a gap (24) results between the piston ring carrier (12) and the guide surface (22), wherein the piston skirt (20) and the piston ring carrier (12) are connected to one another via at least one reinforcing rib (32) which extends transversely over the inner piston crown (18).

2. Piston according to the preceding claim, characterized in that the at least one reinforcing rib (32) extends in the middle section in the axial direction from the inner piston crown (18) to such an extent that a piston pin flange (28) is formed in the reinforcing rib (32).

3. Piston according to any one of the preceding claims, characterized in that the piston ring carrier (12) is connected with the piston ring carrier (12) via the at least one reinforcing rib (32) and via one or more connecting sections (26) between two guide surfaces (22).

4. Piston according to one of the preceding claims, characterized in that the frame-like structure is formed by two curved guide surfaces (22) and two connecting sections (26) extending between the guide surfaces (22) and in that two reinforcing ribs (32) are respectively formed inside the connecting sections (26).

5. Piston according to one of the preceding claims, characterized in that the piston ring carrier (12) has a recess (34) on a face directed opposite the piston skirt (20) and the at least one reinforcing rib (32) extends transversely through the recess (34) in such a way that it is respectively joined on the outside at the inner face of the recess (34).

6. Piston according to one of the preceding claims, characterized in that the at least one reinforcing rib (32) and/or the at least one connecting section (26) are configured curved in a longitudinal viewing section.

7. Piston according to any one of the preceding claims, characterized in that two piston pin flanges (28) are provided and that each piston pin flange (28) also extends through the strengthening rib (32) corresponding to it.

8. Piston according to any of the preceding claims, characterized in that a thickening (30a,30b) extending in the passage direction of the piston pin is configured on the outside of the piston pin flange (28), which extends over the entire circumference of the piston pin flange (28).

9. Piston according to any of the preceding claims, characterized in that the at least one guide surface (22) has at least one recess (38) which reduces the guide surface (22) to two or more partial guide surfaces (40, 42).

10. A reciprocating piston internal combustion engine with a piston (10) according to any one of claims 1-9.